Automatic cloth-spreading machine



Aug. 28, 1962 F. KIBLER ET AL AUTOMATIC CLOTH-SPREADING MACHINE 5 Sheets-Sheet 1 Filed Sept. 20, 1960 A" m W Wu RL 0 MR MA FH Aug. 28, 1962 F. KIBLER ET AL AUTOMATIC CLOTH-SPREADING MACHINE 5 Sheets-Sheet 2 Filed Sept. 20, 1960 INVENTORS FREDERICK KIBLER HAROLD Z. SHAPIRO Aug. 28, 1962 F. KIBLER ET AL 3,051,475

AUTOMATIC CLOTH-SPREADING MACHINE Filed Sept. 20, 1960 5 Sheets-Sheet 3 INVENTORS FREDERICK KIBLER HAROLD Z. SHAPIRO Aug. 28, 1962 F. KIBLER ET AL AUTOMATIC CLOTH-SPREADING MACHINE 5 Sheets-Sheet 4 Filed Sept. 20, 1960 Mal. 1: 1H;

A INVENTORS. FREDERICK KIBLER HAROLD Z. SHAPoRO Aug. 28, 1962 F. KIBLER ET AL 3,051,475

AUTOMATIC CLOTH-SPREADING MACHINE Filed Sept. 20, 1960 5 Sheets-Sheet 5 FIG. 6A

I N VE NTORS 5250521 (A! Melee ATTOEA/EYS United States Patent AUTOMATIC CLOTH-SPREADING MAC Frederick Kibler, Whitestone, N.Y., and Harold Z.

Shapiro, East Orange, N..l., assignors to Spreading Machine Exchange, Inc., New York, N.Y., a corporation of New York Filed Sept. 20, 1960, Ser. No. 57,314 7 Claims. (6]. 270-31) This invention relates generally to machines for spreading and folding cloth in superposed layers on a table for cutting the layers simultaneously into garment pieces, and more particularly to a novel mechanism for reversing the spreader box of such a machine as each layer is completed.

In the garment industry it is customary to mass produce the pattern-pieces necessary for a run of a given model and size of garment by simultaneously cutting such pieces from numerous superposed layers of cloth each of which comprises the material of at least one individual garment. The cloth is obtained in compact condition, usually rolled in a cylinder or sometimes folded in fiat form, and it is then necessary to spread it in elongated superposed layers for the cutting operation. This is done by spreading layers of the cloth longitudinally along a cutting table to the appropriate length, usually of the order of at least several yards, and then folding the cloth back over each such layer in a continually reversing sinuous pattern to spread succeeding layers of the same length thereover, repeating the process until the required number of layers has been accumulated.

In modern times, the well-known automatic clothspreading machine has been developed to perform the function of arranging the material on the cutting table in this manner. Such machines typically have a carriage which holds a supply of cloth and reciprocates longitudinally of the cutting table, and a spreading box mounted on the carriage which engages the cloth and spreads it in layers along the table as the carriage reciprocates. The spreader box has a pair of bight-forming blades on one end and cloth-spreading means on the opposite end. Therefore, the box, which faces in one direction as the carriage traverses through one spreading stroke, must be turned about at the end of that stroke to move the blades into position to make a bight which forms the fold at the end of the current layer, and also to face the op posite way for spreading the next layer during the succeeding oppositely directed traverse of the reciprocating carriage.

Accordingly, there must be a reversing mechanism which turns the spreader box about in response to the arrival of the carriage at each of the opposite limits of its reciprocatory movement. The problems of designing such a mechanism are complicated by the fact that as the pile of superposed cloth layers increases in height the spreader box must be progressively elevated to be able to spread each succeeding layer atop the previous ones. As a result, the reversing mechanism must be arranged to make some sort of self-adjusting driving connection to the spreader box in order to drive the latter through its periodic reversing motion at any of the various different vertical positions which is assumes during the course of the spreading operation.

The problem has been solved to some extent by providing a rotary drive journaled at a fixed location on the reciprocating carriage, and an arrangement of stationary stops fixed to the cutting table and a cam track cooperating therewith to engage the rotary drive as the latter moves with the carriage so as to turn the rotary drive over at the limits of the reciprocatory movement. Then a self-adjusting coupling is provided to connect 3,051,475 Patented Aug. 28, 1962 the fixed rotary drive to the moving spreader box. In the past this coupling has been in the form of a chain drive trained over a quartet of sprockets mounted at the corners of a pantograph linkage. Such complex coupling has never been completely satisfactory, however, chiefly because in practice it has turned out to be overly delicate and sensitive to slight misalignments and therefore difficult to assemble and maintain,

Accordingly, it is an object of this invention generally to provide, for connecting a stationary rotary drive to a moving mechanism such as a spreader box, a self-adjusting coupling which will avoid the disadvantages of previous expedients. In particular it is an object of the invention to provide a coupling of this type which will be relatively simple, sturdy, and flexible enough in operation to compensate for small inaccuracies in the construction and assembly thereof.

In accordance with this invention, there is provided a mechanism for turning the spreader box of a clothspreading machine in each of its various vertical positions, the mechanism comprising a driving crank rotatably mounted at a fixed location on the carriage of the clothspreading machine, means for turning the driving crank over as the carriage reaches the limits of its reciprocation, a driven crank operatively connected to turn the cloth-spreader and to move vertically therewith, lever means, means making a rotary driving connection between the lever means and each of the cranks and permitting sliding motion of the lever means between the cranks to compensate for vertical movement of the driven crank, and means providing a floating pivot mounting the lever means for pivotal movement whereby to transmit turning motion between the cranks and for floating movement in response to vertical movement of the driven crank.

The foregoing brief summary, as well as further features and advantages of the invention, may best be appreciated by reference to the following detailed description of an illustrative embodiment, when read in conjunction with .the accompanying drawings, wherein:

FIG. 1 is a side elevational view of an automatic cloth-spreading machine incorponating a spreader-box reversing coupling in accordance with the present invention;

FIG. 2 is an enlarged side elevational view of the reversing coupling of FIG. 1 in a lowered operating position;

FIG. 3 is a side elevational view similar to FIG. 2, but illustrating the coupling in the position assumed after having been moved to turn over the spreader box, and with parts thereof illustrated in phantom in an elevated openating position to demonstrate the manner in which the coupling adjust for vertical movement of the spreader box;

FIG. 4 is a vertical section taken along the line 44 of FIG. 2;

FIG. 5 is a horizontal section taken along the line 55 of FIG. 2;

FIGS. 6A, 6B and 6C are schematic representations of the spreader box laying down a plurality of layers of textiles; and

FIG. 7 is a schematic and exploded view of the linkage arrangement which functions to sommersault the spreader box at the end of each transverse movement of the device.

Before referring to the details of the present invention, reference is made to FIGS. 6A, 6B and 6C. In FIG. 6A it is seen that a clamp 62 is effective to hold a layer of cloth 22 on the table 10. A spreader box, generally designated by the numeral 28, and being generally of U-shaped configuration (see FIG. 4), including a first leg 58, a

terrelationships of the cam tract 48, the driving crank 90, the driven crank 92, the lever assembly 94, and the spreader box 28, with its associated shaft 30, may be conveniently seen in the exploded view of FIG. 7. It may be often convenient, during the course of the following description, to refer to FIG. 7 for a simplified illustration of the various members of the assemblies even though that figure illustrates some of the individual parts in somewhat distorted configuration.

As best seen in FIGS. 2 and 5, the cranks 90 and 92 include respective identical first crank arms 90 and 100 fixed at one end thereof to ends of the respective shafts 42 and 30 which protrude outwardly from the carriage 14. The crank arms 93 and 100 may be in the form of short, heavy gauge rectangular steel bars formed with appropriate bores to receive the ends of the shafts 42 and 30 respectively and transverse bores receiving keying pins or set screws to lock the crank arms to the shafts for rotation therewith. This construction is sturdy and makes for ready assembly and disassembly. First connecting pins 102 and 104 project outwardly from crank arms 98 and 100 and are spaced from the respective shafts 4-2 and 30 so as to rotate at a radial distance therefrom and thereby make a rotary driving connection to the lever assembly 94-. The pins 102 and 104 are short, thick, steel dowels which may be received in bores formed in the respective crank arms 98 and 100 and also locked in place by set screws or keying pins.

The lever assembly 94 includes a first lever 106 in the form of a sturdy steel bar formed with longitudinally elongated slots 106a and 10619 at opposite ends thereof which receive the first connecting pins 102 and 104 respectively to make a rotary driving connection to the crank arms 90 and 100. The widths of slots 106a and 6b are selected in relation to the diameters of the respective connecting pins 102 and 104 to fit closely thereabout so that rotary motion is transmitted between the crank arms 98, 100 and the lever 106 without a great deal of backlash, yet loosely enough for the connecting pins to be freely slidable along the length of the slots to allow longitudinal motion of the lever without disrupting the rotary driving connection. For reasons which will subsequently be explained, the lever assembly 94 also includes a second lever 107 identical to the first lever 106 and formed with slots 107a and 10712 identical to the slots 106a and 10611.

In order to make rotary driving connections between the cranks 90, 92 and the second lever 107, the first connecting pins 102 and 104 are made long enough to project entirely through the respective slots 106a and 106b, and second crank arms 108 and 109, identical to the first crank arms 98 and 100, are fixed at one end to the outwardly projecting ends of the pins 102 and 104 in the same manner that the pins are fixed to the first crank arms 98 and 100. Second connecting pins 110 and 111, identical to the first connecting pins 102 and 104-, are similarly fixed to the other ends of the second crank arms 100 and 109 respectively at a radial distance from the respective shafts 42 and 30, and project outwardly from these crank arms to make the same sort of longitudinally slidable rotary driving engagement with slots 107a and 1071) respectively that the first connecting pins 102 and 104- make with the slots 106a and 1062: respectively.

The pantograph linkage 96 may be any four bar linkage connected between the cranks 90 and 92 in a manner to support the lever assembly 94 for motion about a pivot substantially midway between the cranks, thus assuring that the arms of the lever assembly 94 connected to the respective cranks 90 and 92 will be approximately equal. The linkage 96 includes four bars 112, 113, 114, and 115 pivotally connected to form a diamond-like arrangement by means of pivot pins 116, 118, 120 and 122 located at the corners of the diamond. The bars 11-2,

'and 113 have integral extensions 11 2a and 113a respec tively extending downwardly to make pivotal connections 0 to the drive shaft 42 and the spreader box shaft 30 respectively to mount the diamond linkage therebetween.

The lowermost pivot pin 120 of the diamond linkage extends pivotally through the levers 106 and 107 midway between the elongated slots at their opposite ends, thus mounting the levers for rotation about the pivot pin in response to the driving of crank 90. The spatial arrangement which permits the diamond linkage 112-115 and the cranks 90, 9 2 to be connected to levers 106 and 107 in this manner is best seen in FIG. 5. One of the upper diamond linkage bars 112 occupies a plane nearest the frame 16, and is spaced therefrom by a washer 124 surrounding the shaft 4 2. The other upper diamond linkage bar 113 is located in the next plane outwardly therefrom, and is spaced from the frame 16 by a washer 126 surrounding shaft 30 which has an axial thickness approximately equal to the axial thickness of washer 124 plus the thickness of bar 112 in order to properly position the bar 113. The next plane outwardly of bar 113 is occupied by the first crank arms 98 and 100, these being of equal thickness. A Washer 128 having a thickness approximately equal to that of the bar 1 13 is located in the plane of that bar surrounding shaft 42 to properly position crank arm 98 in the plane of crank arm 100. The next plane outwardly thereof is occupied iby the first lever 106, the succeeding plane by the second crank arms 108 and 109 which are also of equal thickness, and the plane after that by the second lever 10-7. The lower diamond linkage bars 114 and 115 are interspersed with the levers 106 and 107, the bar 115 being in the plane between the upper diamond linkage bar 112 and first lever 106, and the bar 114 being in the plane between the first and second levers 106 and 107. A washer 130 having an axial thickness equal to the thickness of one of the first crank arms 98 or plus the thickness of the first lever 106 surrounds the pivot pin to properly position the bar 114.

The lengths of the upper diamond linkage bars 112 and 113 between pivot pins 116-122 and 116118 respectively are equal, as are the lengths of the lower diamond linkage bars 113 and 114 between pivot pins 122--120 and 118-120, and the lengths of the lower extensions 112a and 113a between pivot pin 122 and shaft 4-2 and between pivot pin 118 and shaft 30, these lengths being so chosen that the lower pivot pin 120 is located along the line between shafts 42 and 30. The geometry of the described arrangement is then such that the pivot pin 120 and the lever assembly 94 centrally mounted thereon are centered between the shafts 42 and 30. In addition, the cranks 90 and 92 are arranged so that the first connecting pins 102 and 104 are the same radial distance from their respective shafts 42 and 30 and are displaced therefrom in opposite directions, the same being true of the second connecting pins 110 and 111. In the position illustrated in FIGS. 2 and 5, for example, the first connecting pins 102 and 104- are displaced to the left and right respectively, and the second connecting pins 110 and 111 are displaced respectively downwardly and upwardly, from the respective shafts 42 and 30. Consequently, the lengths of the arms of the first lever 106 measured from the respective first connecting pins 102 and 104 to the centrally positioned pivot pin 120 are equal, the same being true of the second lever 107 and the second connecting pins 110 and 11 1 in engagement therewith.

With the described arrangement, rotation of the driving crank 90 causes the connecting pins 102 and 110 thereof to rotate the levers 1'06 and 107 about the pivot pin 120, which in turn drives the connecting pins 104 and 111 of the driven crank 92 to produce an identical rotation thereof. This may be appreciated by a comparison of the operating position illustrated in FIGS. 2 and 5, in which the carriage 14 is at the left hand limit of its reciprocation and the cam follower pin 46 is consequently to the left of the peak 48a of cam track 48, with the op- ,rnove longitudinally of the lever 106.

crating position of FIGS. 1 and 3 in which the carriage has been traversed to the right hand limit of its reciprocation and the cam follower pin has traversed the peak of the cam track from left to right to turn the driving crank 90 over in a counterclockwise direction. It is seen that such motion results in driving the lever assembly 94 so that the driven crank 92 is also turned over in a counterclockwise direction for rotating the spreader box shaft 30 and thus reverse the spreader box 28. An oppositely directed traverse of the carriage 14 causes clockwise rotation of the cranks 90 and 92.

As the driving crank 90 turns from the position of FIGS. 2 and 5, the connecting pin .102 will move substantially perpendicularly to the longitudinal axis of lever 106, thus rotating that lever clockwise about pivot 120 and thereby causing a similar movement of the connecting pin 104 perpendicularly to the longitudinal axis of the lever 106. The translational movements of the opposite ends of lever 106 are in opposite directions, i.e. up at the left and down at the right, because the rotary motion of the lever is about the centrally located pivot. But this is canceled by the fact that the driving crank connecting pin 102 and the driven crank connecting .pin 104 are on opposite sides of their respective axes of rotation, the shafts 42 and 30. This results in rotation of the driven crank 92 in the same angular sense as that of the driving crank 90, i.e. counterclockwise in the example given. The fact that the opposite arms of the levers 106 are equal assures the transfer of motion from the driving crank connecting pin 102 to the driven crank connecting pin 104 in a 1:1 relationship.

When the connecting pins 102 and 104 are moving perpendicularly to the longitudinal axis of the lever 106, they are then in maximum motion-transferring relationship thereto. After the cranks 90 and 92 have completed approximately one quarter of a revolution, with still about another quarter of a revolution to go for reversing the spreader box 28, the connecting pins 102 and 104 are then in a dead center position wherein they When this stage is reached, the rotation of the cranks 90 and 92 moves the respective connecting pins 102 and 104 thereof along the length of the respective longitudinal slots 106a and Gb instead of against the walls thereof, and therefore the connecting pins then transfer substantially no motion to and from the lever 106. As a result, the driving crank connecting pin 102 must be turned past this dead center position before it will again begin to drive the lever 106, and when it does so, having traveled over center, it will thenceforth rotate the lever in the counterclockwise direction, i.e. opposite to its direction of rotation before traveling over center. The driven crank connecting pin "-104, which is in a position similar to that of the driving crank connecting pin 102, reaches its deadcenter position simultaneously therewith, after which no motion is transferred from lever 106 to the driven crank connecting pin 104 and the driven crank 92 becomes temporarily stalled at 'dead center. This raises the possibility that when the lever 106 begins to rotate in the opposite angular direction such motion might then cause the driven crank 92 to rotate in the wrong, i.e. the clockwise direction du-ring the ensuing quarter turn, thus sending the driven crank back to its original position instead of completing the necessary hal-f turn to reverse the spreader box 28.

It is for this reason that the second lever 107 and second connecting pins 110 and 111 are provided. These members exactly duplicate the driving relationship of the first lever 106 and connecting pins 102 and 104-, by virtue of their identical construction and arrangement. The second connecting pins 110 and 111, however, are angularly displaced about the respective shafts 42 and 30 from the respective first connecting pins 102 and 104 of the same crank 90 or 92, this being achieved by securing the first and second crank arms 98, 108 and 100, 109 of each crank 90 and 92 to the respective first connecting pins 102 and 104 thereof at an angle to each other. Consequently, the first set of connecting pins 102 and 104 and the second set of connecting pins 110 and 111 reach any given operating stage, and in particular the dead center stage, at different phases of the rotations of the cranks and 92. The optimum angular displacement between them is the one which places the first connecting pins 102 and 104 in maximum motion-transferring relationship to the first lever 106 when the second connecting pins 110 and 111 are in minimum motion-transferring relationship to the second lever 1'07, and vice-versa. It is apparent from the geometry of the structure that this angle is equal to the arccosine of: the distance from the axis of a shaft, =e.g. shaft 42, to the axis of an associated connecting pin, e.g. pin 110, divided by the distance from the axis of that shaft to the axis of the central pivot pin 120. With any angular displacement between the sets of connecting pins, however, whether it is the optimum one or not, at all stages of the rotation of the driving crank 90 at least one set of connecting pins will be in a position other than dead center so as to keep the driven crank 92 rotating in the same angular direction and thereby preclude any possibility of a reversal owing to the ambiguity of a dead center position of the other set of connecting pins.

As best seen by comparing the solid and broken-line views of FIG. 3, the slidable nature of the connection between the lever assembly 94 and the cranks 90 and 92 and the action of the diamond linkage 112115 cooperate to preserve the driving relationship between the cranks and the lever assembly as the driven crank 92 rises during elevation of the block 32, spreader box shaft 30, and spreader box 28 by the drive chain 34 and sprockets 36. As driven crank 92 rises, the distance between that crank and the driving crank 90 increases. This is compensated for by sliding of the connecting pins 102, 104, 110, and 111 outwardly from the central pivot pin 120 longitudinally along the respective slots 106a, 106b, 107a, and 10712 of the lever assembly 94.

The upward motion of spreader box shaft 30 raises the right hand linkage bar 113 pivotally connected thereto, which has the effect of rotating the entire pantograph linkage 96 upwardly about the drive shaft 42 to which the left hand linkage bar 112 is pivotally connected and opening up the linkage to make the diamond-shaped structure 112-115 Wider and shallower as indicated by the broken-line view of FIG. 3. This raises the lower pivot 'pin 120 on which the lever assembly 94 is carried, thus rotating the lever assembly so that the right hand end thereof moves upwardly along with the driven crank 92, the lever arms 106 and 107 rotating counterclockwise about their respective driving crank connecting pins 102 and 104.

As the shape of the diamond linkage 112-115 changes the equality of length between the upper bars 112 and 113, between their extensions 112a and 113a, and between the lower bars 114 and 115 assures that the lower pivot pin 120, carrying the lever assembly 94, floats with the pantograph linkage 96 in response to motion of the shaft 30 in such a way as to remain always centered along the line between the two shafts, 42 and 30.

Then the fact that the connecting pins of each set 102 and 104 or 110 and 111 are positioned in matched relationship to their respective shafts 42 and 30 as previously described assures that the lengths of the arms of the lever assembly 94 measured from the pivot pin to the respective connecting pins of each set will remain equal although increasing as the connecting pins slide outwardly along the longitudinal slots 106a, 106b, 107a, and 10%. This preserves the 1:1 correspondence between the motions of the driving crank connecting pins 102, 104 and the driven crank connecting pins 110, 111 respectively as the driven crank 92 is elevated.

It will therefore be appreciated that a reversing coupling in accordance with this invention is simply and sturdily constructed, and functions in such a manner that minor inaccuracies in manufacture or assembly are not critical, while nevertheless meeting the operating requirements of continuous transmission of rotary motion between shafts separated by a varying distance.

While preferred embodiments of the invention have been shown and described herein, it is obvious that numerous additions, changes and omissions may be made therein without departing from the spirit and scope of the invention.

What we claim is:

1. In a machine for spreading cloth in superposed layers including a carriage reciprocable between limits and a device for spreading said cloth fixed on a first shaft mounted for rotation on said carriage to turn said clothspreading device about at the limits of reciprocation thereof and for movement on said carriage to raise said cloth-spreading device as the height of said superposed layers increases; a mechanism for turning said clothspreading device in different vertical positions thereof comprising a driving crank, a second shaft rotatably mounting said driving crank at a fixed location on said carriage, means for rotating said second shaft for turning said driving crank over as said carriage reaches the limits of reciprocation thereof, a driven crank secured to said first shaft to turn said cloth-spreading device and to move vertically therewith, lever means formed with 1ongitudinal slots at opposite ends thereof, both of said cranks including connecting pins projecting therefrom at locations radially offset from the respective centers of rotation thereof and engaging said respective longitudinal slots to make a rotary driving connection between said lever means and each of said cranks and permitting sliding motion of said lever means between said cranks to compensate for vertical movement of said driven crank, and a floating pivot mounting said lever means for pivotal movement whereby to transmit turning motion between said cranks and positioned for floating movement whereby to center said floating pivot between said first and second shafts in different vertical positions of said driven crank.

2. In a machine for spreading cloth in superposed layers including a carriage reciprocable between limits and a device for spreading said cloth fixed on a first shaft mounted for rotation on said carriage to turn said cloth-spreading device about at the limits of reciprocation thereof and for vertical movement on said carriage to raise said cloth-spreading device as the height of said superposed layers increases; a mechanism for turning said cloth-spreading device in different vertical positions thereof comprising a second shaft rotatably mounted at a fixed location on said carriage, a driving crank fixed to said second shaft, means rotating said second shaft for turning said driving crank over as said carriage reaches the limits of reciprocation thereof, a driven crank fixed to said first shaft to turn said cloth-spreading device and to move vertically therewith, lever means formed with longitudinal slots at opposite ends thereof, both of said cranks including connecting pins projecting therefrom at locations radially offset from the respective centers of rotation thereof and engaging said respective longitudinal slots of said lever means to make a rotary driving connection thereto, said connecting pins and said lever means being so arranged as to be in maximum motion-transferring relationship to each other at different phases of the rotation of said cranks, said connecting pins being sized to permit longitudinal sliding motion of said lever means between said cranks to compensate for vertical movement of said driven crank, a pantograph linkage connected between said first and second shafts, and a floating pivot mounting said lever means on said pantograph linkage for pivotal movement whereby to transmit turning motion between said cranks and positioned for floating movement with said pantograph linkage whereby to center said floating pivot between said first and second shafts in different vertical positions of said driven crank.

3. A mechanism according to claim 2 wherein said respective cranks include respective first crank arms fixed to said respective shafts, respective first connecting pins projecting from said respective first crank arms, respective second crank arms fixed to said respective first connecting pins, and respective second connecting pins projecting from said respective second crank arms, said lever means including a first lever having respective longitudinal slots at opposite ends thereof receiving said respective first connecting pins, and a second lever having respective longitudinal slots at opposite ends thereof receiving said respecive second connecting pins, said first and second connecting pins of each crank being angularly offset from each other so as to be in maximum motion-transferring relationship to said respective levers at different phases of the rotation of said cranks.

4. In a cloth-spreading machine of the type wherein cloth is spread in superposed and folded layers by the movements of a reciprocating carriage and a rotating cloth-spreading device mounted on said carriage for vertical movement, actuating means for rotating said clothspreading device comprising a driving shaft rotatably mounted on said carriage at a fixed location, a driving crank secured thereto, a driven shaft operatively con nected to said cloth-spreading device and movable vertically therewith, a driven crank secured thereto, means to rotate said driving shaft, and means for interconnecting said driving crank to said driven crank for transmitting rotating motion irrespective of the vertical position of said driven crank comprising a pair of crossed links pivotally interconnected intermediate their ends, a floating pivot mounting said pivotal interconnection intermediate said first and second shafts, and sliding connections including complementary pins and slots between said cranks and said crossed links.

5. In a machine for spreading cloth in superposed layers including a carriage mounted for reciprocal movement between limits and a device for spreading said cloth mounted on said carriage for turning movement at the limits of reciprocation of said carriage and for vertical movement on said carriage to raise said clothspreading device as the height of said superposed layers increases; a mechanism for turning said cloth-spreading device comprising a driving crank rotatably mounted at a fixed location on said carriage, means for rotating said crank as said carriage reaches the limits of its reciprocation, a driven crank operatively connected to said clothspreading device and mounted to move vertically therewith, a pair of levers pivotally interconnected intermedi ate their ends, means mounting said pivotal interconnection at a location equidistant from said driving crank and said driven crank, means slidably interconnecting said driving crank and said levers at one end thereof and said driven crank and said levers at the other end thereof providing a rotatable driving connection between said driving and driven crank, said slidable interconnecting means permitting longitudinal sliding motion between said cranks to compensate for vertical movement of said driven crank with said cloth-spreading device and to provide rotation of said driven crank at various vertical locations as a result of rotation of said driving crank.

6. In a machine for spreading cloth in superposed layers including a carriage mounted for reciprocal movement between limits and a device for spreading said cloth mounted on said carriage for turning movement at the limits of reciprocation of said carriage and for vertical movement on said carriage to raise said clothspreading device as the height of said superposed layers increases; a mechanism for turning said cloth-spreading device comprising a driving crank rotatably mounted at a fixed location on said carriage, means for rotating said crank as said carriage reaches the limits of its reciprocation, a driven crank operatively connected to said clothspreading device and mounted to move vertically therewith, a pair of levers pivotally interconnected intermedi* ate their ends, means mounting said pivotal interconnection at a location intermediate said driving crank and said driven crank, means slida-bly interconnecting said driving crank and said levers at one end thereof and said driven crank and said levers at the other end thereof providing a rotatable driving connection between said driving and driven crank, said slidable interconnecting means permitting longitudinal sliding motion between said cranks to: compensate for vertical movement of said driven crank with said cloth-spreading device and to provide rotation of said driven crank at various vertical locations as a result of rotation of said driving crank.

7. In a machine for spreading cloth in superposed layers including a carriage reciprocably mounted for movement between limits and a device for spreading said cloth mounted on said carriage for turning movement at the limits of reciprocation of said carriage and for vertical movement on said carriage to raise said cloth-spreading device as the height of said superposed layers increases, a mechanism for turning said cloth-spreading device comprising a driving crank rotatably mounted at a first location on said carriage, means for rotating said crank as said carriage reaches the limits of its reciprocation, a driven crank operatively connected to said clothspreading device and to move vertically therewith, lever means formed with longitudinal slots at opposite ends thereof and pivotally interconnected intermediate said ends, means mounting said pivotal interconnection at a location intermediate said driving crank and said driven crank both of said driving and driven cranks including connecting pins projecting therefrom at locations radially offset from the respective centers of rotation thereof and engaging said respective longitudinal slots of said lever means to make a rotary driving connection between said driving and driven crank, said connecting pins being sized to permit longitudinal sliding motion of said lever means between said cranks to compensate for vertical movement of said driven crank and to provide rotation of said driven crank at various vertical locations as a result of rotation of said driving crank.

Gilbert et al. June 1, 1948 Gilbert et a1. Aug. 29, 1950 

